Tabulating device for an accounting or like machine



Sheet INVENTORS ALESSANDRO CORTONA PIERO MUSSO tented Nov. 24, 1970 Sheet INVEN ALESSANDRO ai JNA PIERO MUSSO gl u 1| 1| u u u u AGENT atented New 2, 3,542,285

Sheet 3 018 63a 63b ear 3 276a 276b 276d 27sr F lg. 6

INVENTORS ALESSANDRO CORTONA Pl E R0 MUSSO atented Nbv. 24,

Sheet 4 of8 INVENTORS ALESSA N DRO CORTONA PIERO MUSSO atented Nov. 24, 1970 Sheet INVENTORS ALESSANDRO CORTONA PIERO MUSSO Sheet INVEN ALESSANDRO b gm PIERO MUSSO atnted Nov. 24, 1976 Sheet Qm 3m 5% l mmm INVENTORS ALESSANDRO CORTONA PfERO MUSSO Patented Nov. 24, 197@ Sheet INVENT R5 ALESSANDRO COQRTONA PIERO MUSSO TABULATING DEVICE FOR AN ACCOUNTING R LIKE MACHINE The present invention relates to a tabulating device for an accounting machine or other office machine comprising a printing device, a support for the paper and a carriage adapted to be shifted transversely to change the relative position between the support and the printing device.

In known tabulating devices the travel of the carriage is generally arrested successively by stops preset on the conventional tabulating bar. It is also known however to use the stop at which the carriage has been arrested to control further movement of the carriage. this stop selecting a group of stops for the following stopping positions of the carriage. The tabulation effected in this way nevertheless remains inflexible and complicated. The object of this invention is to overcome such drawbacks.

According to the invention there is provided a tabulating device for controlling thernovement of the carriage of an accounting or other office machine, comprising a first store adapted to indicate from time to time the current position of the carriage, a second store adapted to beset to indicate a desired position to be reached by the carriage, comparing means for comparing the indications given by the two stores and driving means controlled by the comparing means for shifting the carriage until the said indications are equal.

Each of the stores can comprise a series of elements adapted to represent the positions in a code having combinations of binary units, each element ofthe first store being constitutcd by a pair of parts adapted to representthe two states of each binary unit. each element of the second store being constituted by a member having two positions, the comparison means comprising a series of pairs of sensing members adapted to sense the said parts and the said members simul- I taneously. v

The invention will be described in more detail, by way of example. with reference to the accompanying drawings, in which:

FIG. 1 is a partial'plan view of an accounting machine incorporating a tabulating device according to the invention;

FIGS. 2 and 3 are further partial plan views of the tabulating device;

FIG. 4 is a partial section on the line IV-IV of FIG. 2; FIG. 5 is a partial section on the line V-V of FIG. 3; FIG. 6 is a partial section onthe iine VI-VI of FIGS. 2 and FIG. 7 is a partial section of a detail on the line VII-VII of FIG. 2; FIG. 8 is a partial front view of a detail of the device;

t abulating FIG. 9 is a rear perspective view from the right ofa detail of the tabulating device;

FIG. 10 is a partial section on the line X-X of FIG. 2; 7 FIG. 11 is a partial section on the line XI-XI of FIG. 3; FIG. 12 is a diagram ofa detail ofthe tabulating device.

OUTLINE DESCRIPTION Before commencing a detailed description of the construction and operation ofthe device a briefoutline will be given of whereupon a first l80 rotation of a control cam shaft 56 takes place. In this 180 rotation sensing levers 33, 34 (FIG. 4) compare the settings ofthe code bars with the earns 63, 64 and the levers for the highest weight bit which is not the same in the desired and actual positions determines whether or not nbuil 126 (FIG. 7) rotates, corresponding to a requirement for tabulation to the left and the right respectively. This bail controls the direction in which connecting rods 136 and 223 (FIGS. 7

and 10) are now moved. The rod 136 couples a shaft 16I (FIG. 9) to the shaft 66 via a bevel gear 181 or 182 depending on the required direction of tabulation. The rod 223 (FIG. 10) presets a lever 226 which carries pawls for arresting the shaft 66. Drive is then imparted to the shaft 161 to start the tabulating movement, terminating the first 180 rotation of the shaft 52.

During the tabulating movement the cams 63, 64 are not sensed; instead the cams 276 and 277 are sensed in conjunctionwith the code bars 26 by levers 251 and 252 (FIG. 5). When the actual position reaches the desired position all levers 251' and 252 withdraw lugs from a bail 283 whose consequent rotatic-n actuates pawls 303, 304 (FIG. 10) on the lever 226..Th ese pawls engage toothed wheels 3306 and 307 on the shaft 66, thus arresting the carriage. A second l80 rotation of the shaft 52 is now instituted, during which the mechanisms are restored to their rest settings.

DETAILED DESCRIPTION OF THE CONSTRUCTION OF THE DEVICE The tabulating device is incorporated in an accounting machine comprising a printing device 15 (FIG. 1) and compris ng a series of four type wheels 16 rotatable selectively about a corresponding horizontal spindle. The wheels 16 are the line spacing of the paper.

The accounting machine also comprises a support movable transversely to change the relative position between the writing device 15 and the platen 17. This support is formed by a carriage 18 on which the device 15 is mounted. The carriage 18 is guided through the medium of four rollers 19 on two transverse bars 20 fixed to two side plates or panels 21 and 22 of the machine. Thecarriage 18 moves parallel to the platen 17, with respect to which it can adopt 128 different positions. The movement of the carriage is controlled by a program device not shown in the drawings, for example a magnetic tape adapted to supply in parallel signals coded in a code in the form of a combination of seven binary units or seven bits, which represent the position that the carriage must reach.

These signals control a store adapted to be set according to the position required for the carriage 18. This store comprises a series of seven code bars 26 (FIG. 6) which can turn in the frame of the machine. In response to these signals, the code bars 26 are brought selectively into two different positions. On reception of a zero signal, the corresponding code bar 26 is brought into the position shown in FIG. 6, while on reception of a one signal it is rotated clockwise and brought into the position shown in dashes for the left hand code bar in FIG. 6.

On each code bar 26 there is fixed a lug 27 in which is formed a notch 28 ('FIG. 4) having a first shoulder 31 and a second shoulder 32.

The tabulating arrangement is equipped with comparison means adapted to compare the current position of the carriage with the position to be reached. The comparison means comprise a series of seven pairs ofsensing members or levers 33, 34 pivoted on a fixed spindle 38 and associated with the seven code bars 26. Each lever 33 and 34 is provided with a projection 36 and 37, respectively, adapted to cooperate with the shoulder 31 of the corresponding lug 27. Thus on reception of a zero the shoulder 31 is located in the path of the projection 36 (FIG. 6) and on reception of a one it is located in the path of the projection 37.

The levers 33, 34 normally bear under the section of individual springs 39 (FIG. 4) against a universal bar 41 carried by apnir of cranks 42 pivoted on the spindle 38. The cranks 42 are connected by means of a connecting rod 43 to a lever 44 pivoted on a spindle 46. The lever-44 has two arms 47 and 48 cooperating with two earns 49 and 51, respectively, having 57 and normally held disengaged by a lug 55 of a lever 60 pivoted on a fixed spindle 65. When the clutch 57 is engaged, the shaft 56 is rotated anticlockwise for one revolution and causes the shaft 52 to rotate clockwise through 180.

The tabulating arrangement moreover comprises another store adapted to indicate from time to time the current position of the carriage 18 This store comprises a series of seven elements each constituted by a pair of cams 63a, 64a to 633, 64g (FIG. 6) adapted to represent the two states of each binary unit of the combination relating to the current position of the carriage 18. The pairs of cams 63a, 64a to 633, 643 are divided into two groups. The first group, comprises the pair of cams 63a, 64a to 63c, 64c, which are fixed on a common shaft 66 rotatable in the frame of the machine. The second group of cams comprises the pairs of cams 63f, 64f and 63g, 64g,which are fixed on a sleeve 67 rotatable on the shaft 66.

' The profile of each of the cams 63a to 63g is formed by alternate teeth and recesses: a tooth indicates that the corresponding binary digit is one and a recess indicates that such binary digit is zero. The profile of each cam 64a to 643 is complementary to that of the associated cam 63a to 633. The presence of a recess on a cam 64a to 643 confirms that the corresponding binary digit is one, while the presence of a tooth on a cam 64a to 643 confirms that such digit is zero. The profiles are illustrated in FIG. 12.

The cams 63a, have a profile constituted by sixteen teeth and sixteen recesses each extending over an arc of 11 15'. The cams 63b, 64b (FIG. 12) relative to the bit of weight 2 have eight teeth and eight recesses each extending over an arc of 22 The cams 63c, 64c relative to the bit of weight 4 have four teeth and four recesses each extending over an arc of 45; the cams 63d, 64d

relative to the bit of weight 8 have two teeth and two recesses each extending over an arc of 90; the cams 63c, 64c relative to the bit of weight sixteen have one tooth and one recess each extending over an arc of 180.

On the shaft 66 (FIG. 3) there is fixed a gear 68 in mesh with a gear 69 of equal diameter fixed on a shaft 71 rotatable in the frame of the machine. On the shaft 71 there is fixed an arm 72 constituting the driving part of a Geneva motion. The arm 72 is equipped with a pin 70 adapted to cooperate with a series of radial slots 75 disposed at intervals of 60 from one another in a disc 73 forming the driven part of the Geneva motion and. fast with the sleeve 67. The disc 73 is therefore rotated through 60 at each revolution of the shaft 66.

The two pairs of cams 63f, 64f and 63g, 64g.fixed to the sleeve 67 are distributed only over an arc of 240", so that their complete exploration requires 4 revolutions of the shaft 66. For this reason, in FIG. 12 the profiles of the cams 63a, 64a to 63e, 64c are repeated four times. The cams 63f, 64f (FIG. 12) relate to the bit of weight 32 and are constituted by two teeth and two recesses each extending over an arc of 60. The cams 63g, 64g relate to the bitof weight 64 and are constituted by one tooth and one recess each extending over an arc of 120.

On the shaft 66 there is moreover fixed a drum 76 (FIG. 9)

I provided with a helical groove 77, on which a steel wire 81 is wound clockwise and a steel wire 82 is wound anticlockwise. One end of each of the wires 81 and 82 is secured to the drum 76, while the other ends of the wires 81and 82 are attached to the carriage 18 (FIG. 1), the transverse movement of which is thus caused by a corresponding rotation of the shaft 66. More particularly, the movement of the carriage 18 from the zero position shown in FIG.,1 to position 127 corresponds to a rotation of the shaft 66 by 4 revolutions and therefore to a rotation of .the sleeve 67 (FIG. 11) through 240. There is therefore a one-to-one correspondence between the joint positions of the shaft 66 and of the sleeve 67 and the positions of the carriage 18.

640 (FIG. 4) relative to the bit of weight 1 The disc 73 cooperates with a spring-biased click-stop type of positioning member 74 adapted to engage in the radial slots 75 of the disc 73 to hold the sleeve 67 in position. The distance of the pin (FIG. 11) from the shaft 71 and the radius of the disc 73 are in the ratio of l "3 to each other, so thatsince the pin 70 engages a slot when the latter is inclined at 30 with respect to the line joining the shafts 66 and 71, the arm 72 is at to the slot at the instant of engagement, as shown in dash lines in FIG. 11. Consequently, the distance of the pin 70 from the shaft 71 is one-half of the distance between the shafts 66 and 71, so that when the pin 70 is located on the line joining the shafts 66 and 71 the transmission ratio thus comes to be 1 l.

When the carriage 18 is in the zero position, the arm 72 is alined with a slot 75 of the disc 73, as a result of which the shaft 66 causes the sleeve 67 to rotate at the same angular velocity. The same condition is repeated when the carriage 18 passes from position 31 to position 32, from position 63 to position 64, from position to position 96 and when it passes through position 127. These positions correspond to the positions in which the cams 63f, 64f and 63g. 64g mounted on the sleeve 67 pass from a tooth to a recess or vice versa.

The ,tabulating device comprises a series of seven sensing members adapted to determine the direction of movement required of the carriage 18, each sensing member being constituted by a lever 92 (FIG. 4) pivoted on a fixed spindle 93. The levers 92 are-normally held by the action of individual springs 94 so that they bear against a universal bar 96 carried by a bail97 pivoted on the spindle 93. The bail 97 is moreover provided with two arms 98 and 99 adapted to cooperate with two cams 101 and 102 having complementary profiles and fixed to the shaft 52.

Each lever 92 has a lug 103 adapted to cooperate with a shoulder 104 of the lever 92 relative to the bit of immediately higher weight (see also FIGS. 2 and 3). Each lever 92 is moreover provided with a lug 106 (FIG. 4) adapted to cooperate with a projection 107 of the lever 33 relative to the same bit when this-lever 33 is turned clockwise.

Finally, each lever 92 carries a pin 108 on which there pivots a lever 109 normally bearing under the action of a spring 111 against a stud 112 fixed to the same lever 92. Each lever 109 is provided with a lug 113 flanking the lug 106 and adapted to bear against a projection 114 of the lever 34 relative to the same bit. When the levers 109 are turned clockwise, they cooperate with a universal bar 116 carried by two cranks 117 and 118 (FIGS. 4 and 7) fixed to the spindle 46, which can turn in the frame of the machine. The crank 118 normally bears under the action of a spring 121 against a stud 122 fixed to the frame of the machine.

The crank 118 moreover has an arm 123 adapted to cooperate with a lug 124 of a bail 126 pivoting on a fixed spindle 127. The bail 126 is provided with an arm 128 normally bearing under the action of a spring 129 against a cam 131 fixed to the shaft 52. The bail 126 is moreover provided with an arm 133 connected through the medium of a link 134 to a connecting rod 136 pivoting on a pin 137 of a crank 138 which is fixed ona spindle 139 turning in the frame of the machine. The connecting rod 136 carries a pin 141 normally engaged in a notch 1420f a lever 143 pivoted on the spindle 127 and vbearing under the action of a spring 144 against a cam 146 fixed to the shaft 52. The connecting rod 136 carries a second pin 148 adapted to engage in a notch 149 of a lever 151 also pivoted on the spindle 127 and normally bearing under the action of a spring against a cam 153 fixed to the shaft 52.

On the shaft 139 (FIG. 9) there is moreover fixed another crank 156 equipped with a pin 157 engaged in a groove 158 of a dog coupling 159. This coupling is slidable axially on a shaft 161 rotatable in the frame of the machine, but is angularly fast therewith. The shaft 161 is connected via a friction clutch 162 of knowntype to a continuously rotating driving shaft 163.

The coupling 159 moreover carries two rings 171 and 172 provided with axial dogs 173 and 174 respectively. When the coupling 159 is shifted to the right as viewed from-the front of the machine, (to the left in'FIG. 9), the dogs 173 engage with a toothed rim'176 integral with a sleeve 177 rotatable on the shaft 161. On the other hand, when the coupling 159 is shifted to the left (to the right in FIG. 9), the teeth 174 of the ring 172 engage with a toothed rim 178 integral with a sleeve 179 also rotatable on the shaft 161. Which of the sleeves 177 and 179 is selected determines the direction of movement of the carriage. I

The sleeves 177 and 179' are provided with ring bevel gears 181and 182 respectively, in mesh with a ring bevel gear 183 fixed on a shaft 184 rotatable in the frame of the machine. The shaft 184 is moreover provided with a toothed cylinder 186 meshing with a gear 187 fixed to a sleeve 188 rotatable on a shaft 189, which is rotatable in turn in the frame of the machine. The sleeve 188 is axially slidable on the shaft 189 and is fast with a toothed cylinder 191 meshing with a gear 192 fixed to the drum 76. The toothed cylinders 186 and 191 are of such length as to remain always in mesh with the corresponding gears 187 and 1-92. The sleeve 188-is moreover provided with a tooth 193 normally engaged in a crown wheel 194 fastened to the shaft 189. The shaft 189 is adapted to be rotated in known manner by a step-by-step advancing device to control the normal'character spacing of the carriage 18. The mechanism now to be described determines whether the carriage is driven for this purpose by the shaft'l89 or whether the carriage is driven by the sleeve 188 in order to effect tabulation.

On the shaft 52'there is fixed a cam 201 (FIG. 8) cooperating with a lever 202 pivoted on the spindle127 and normally bearing against the camunder the action of a spring 203. The

lever 202 is connected to a link 204 provided with a slot 206 (FIG. 9) in which is engaged a pin 207 of a lever 208 pivoted on a fixed spindle 209. The pin 207 is normally so held with the aid of a spring 211 (FIG. 9) that it bears against the upper end of the'slot 206. The lever 208 terminates in a can slot 212 in which is engaged a'pin 213 of a lever 214 fixed on a spindle 216 which can turn in the frame of the machine. On the spindle 216 there is fixed a second lever 217 equipped with a pin 218 engaged in a groove 219 in the sleeve 188. The pin 218 normally holds the sleeve-188 in the position shown in FIG. 9.

The bail 126 (FIG. is provided with another arm 221 connected through the medium of a link 222 to a connecting rod 223 pivoting on a pin 224 of a three-armed lever 226 pivoted on the shaft 66. The connecting rod 223 is provided with a pin 227 normally engaged'in a notch 228 of a lever 229 pivoted on the spindle 127. The lever 229 is provided with two projections or extensions 231 and 232 cooperating with two cams 233 and 234 fixed on the shaft 52. The two cams 233 and 234 have complementary profiles, except for a short are located 180 from the inoperative position shown in FIG. 10, where the cam 233 has a recess 236.

' The connecting rod 223 carries a second pin 237. adapted to engage in a notch 238 of a lever 239, but normally disengaged therefrom. The lever 239 is fulcrumed onthe spindle 127 and is provided with two projections 241 and 242 normally bearing against two cams 243 and 244 fixed on the shaft 52. The two cams243 and 244 also have complementary profiles, except for a short arc located 180 from the inoperative position, where the cam 243 has a recess 246;

The tabulating arrangement comprises another series of sensing members which is constituted by seven pairs of levers 251 and 252 (FIG. 5) associated with the code bars 26 and pivoted on the spindle 38. On reception of a zero a projection 254 of the lever 252 is located in correspondence with the shoulder 32 of the corresponding lug 27 and, on reception of a one, a projection 253 of the lever 251 is located in correspondence with the same shoulder 32. Each of the levers 251 and 252 normally bears under the action of a spring 256 against a universal bar 257 carried by a pair of cranks 258 (FIGS. 2 and 3) which can turn on the spindle 38. The rear crank 258 (FIG. 5) is connected by means of a connecting rod 261 to a lever 262 pivoted on the spindle 46 and provided with two arms 263 and 264 cooperating with two cams 266 and 267 having complementary profiles and fixed to the shaft 52.

On each lever 251, 252 there is mounted a cam follower roller 273, 274, respectively, adapted to sense a cam 276a, 277a to 276g, 277g (FIGS. 2 and 3). The first five pairs of cams 276a, 2770 to 2762, 277e(FIG. 2) are fixed on the shaft 66, alternating with the cams 63a, 64a to 63c, Me, and the last two 'pairs 276f, 277] and 276g, 277g are fixed on the sleeve 67, these alternating with the cams 63f, 64f and 63g, 64g. The profile of each cam 276a to 276g is similar to that of the cam 63a to 633 relative to the same bit, while the profile of each cam 277a to 277g is similar to that of the corresponding cam 64a to 643. The two flanks of each tooth of the cams 276 and 277, however, are inclined and chamfered.

Each lever 251, 252 (FIG. 5) is moreover provided with a projection 281 and 282, respectively, adapted to cooperate with an edge 280 of a bail 283 provided with two arms 284 and 285 (FIGS. 2 and 3) pivoted on two fixed pins 286. The edge 280 of the bail 283 is in the form of a series of steps comprising one step for each bit, the steps receding towards the bits of lower weight.

The arm 285 (FIG. 5) of the bail 283 is provided with a pin 287 in engagement with a slot 291 in a connecting rod 292 and is biased anticlockwise by a spring 288. The connecting rod 292 is pivoted on a lever 293 pivoted in turn on the spindle 46 and is provided with a spring 294 which holds the lever 293 bearing against'a cam 296 fixed on the shaft 52. The arm 284 (FIG. 10) of the bail 283 is connected via a connecting rod 297 to a lever 298 pivoted on a pin 299 fixed to the lever 226. On the pin 299 there are pivoted two pawls 303 and 304 normally bearing under the action of two springs 302 against a stud 301 on the lever 298. The two pawls 303 and 304 have their stop profiles 300 and 305, respectively, in the same radial plane and are adapted to engage two saw-toothed wheels 306 and 307, respectively, of opposite directions and having a pitch corresponding to the distance between two adjacent positions of the carriage 18. The two wheels 306 and 307 are fixed on the shaft 66 and have the stop profiles of their teeth in the same radial plane.

The lever 226 moreover carries a pin 311 on which there is pivoted a connecting rod 312 provided with a slot 313 sliding on a fixed spindle 314. The connecting rod 312 has two projections 316 and 317 adapted to engage two studs 318 and 319, respectively, fixed to a lever 321 pivoted on the spindle 314. The lever 321 is connected via a link 327 to a piston 324 of a pneumatic brake or dash pot 323 and is normally held in the position shown in the drawing by a spring 322.

The clutch 57 controlling the rotation of the cam shaft 52 is controlled by a start electromagnet 330 which is normally deenergized and is adapted then to cause a pallet 331 to turn clockwise. The pallet 331 is pivoted on a fixed spindle 332 and is normally so held by a spring 334 that it bears against a fixed stop 333. The pallet 331 is moreover provided with a lug 335 against which there normally bears a lever 336 pivoted on a fixed spindle 337. The lever 336 is provided with a notch 338 in which there is engaged a pin 339 of a lever 341 pivoting on the shaft 65. The lever 341 is adapted to cooperate under the action of a spring 342 with a cam 343 fixed on the shaft 52. The lever 336 is provided with a pin 346 against which a lever 348 pivoting on the spindle 337 normally bears under the action of a spring 347. The lever 348 has a shoulder 349 against which a lug 352 of the lever 60 normally bears under the action of a spring 351. The lever 60 is provided with a pin 353 adapted to cooperate with a cam 354 fixed on the shaft 56.

Another lever 361 having a shoulder 362 adapted to be brought above the lug 352 is moreover pivoted on the spindle 337. The lever 361 carries two pins 363 and 364 adapted to cooperate with two projections 367 and 368, respectively, of a connecting rod 369 and is normally held in the position shown in the drawing by a spring 366. The connecting rod 369 is provided with a slot 371 slidable on the spindle 337 and is pivoted to the lever 226.

On the shaft 52 there are moreover fixed two cams 376 and 377 (FIG. 8) having complementary profiles and cooperating with two arms 378 and 379, respectively, of a lever 381. The latter is pivoted on the spindle 127 and is connected via a connecting rod 383 to a crank 384 fixed on a spindle 386 which can turn in the frame of the machine. Also fixed on the spindle 386 is another crank 387 equipped with a pin 388 onwhich there pivots a T-shaped link 389 (FIG..9). The link 389 is connected via two arms 391 and 392 to two links 393 and 394,

- respectively. The link 393 is connected to a lever 396 fast DETAILED DESCRIPTION OF OPERATION OF THE A DEVICE A tabulation operation is ordered by the program, which sends a group of signals representing in the 7-bit binary code the position which the carriage 18 (FIG. 1) must reach. Each of these signals then sets the corresponding code bar 26 (FIG. 6) via'electromagnets in known manner in such a way that if the value of the corresponding bit is zero the shoulder 31 (FIG. 4) of the lug 27 is brought into correspondence with the projection 36 of the lever 33 and if the value of the corresponding bit is one the shoulder 31 is brought into correspondence with the projection 37 of the lever 34. Equally, the shoulders 32 are brought into correspondence with the projections 253 of the le'vers 251 if the value of the correspondingbit is zero and'into correspondence with the prothrough the medium jections 254 of the levers 252 if the value of the corresponding bit is l.

The program moreover transmits a signal energizing the start electromagnet 330, which causes the pallet 331 (FIG. to turn clockwise and be brought into the position shown in dash lines in the drawing. The spring 342 now causes the lever 341 to turn anticlockwise until it bears against the cam 343 and, through the medium of the pin 339, causes the lever 336 to turn clockwise. The pin 346 thus releases the lever 348 which, under the action of the spring 347, follows the rotation of the-lever336 and releases the lug 352 of the lever 60 from the shoulder 349. The spring 35l'now causes the lever 60 to turn anticlockwise until the pin 353 bears against the cam 354. The lug 55 therefore releases the clutch 57, which produces a 360 cycle of the main shaft 56. Through the gears 54 and 53,

. the main shaft rotates the shaft '52 through 180. At the beginning of the cycle, the two cams 49 and 51 (FIG. 4) on the shaft 52 cause the lever 44 to ,turn clockwise and shift the connecting rod 43 to the right. The two cranks 42 are turned clockwise, as a result of which the universal bar 41 releases the levers 33 and 34. The springs 39 tend to cause the levers 33 and 34 to turn clockwise and they are stopped selectively by the shoulders 31 of the lugs 27. More precisely, for each bit only the lever 33 or the lever 34 can turn. The assembly of levers 33 and 34 which turn represents in code the position that the carriage 18'must reach.

As has already been seen, the profile of the cams 63 and 64 in correspondence with the teeth 61 and 62 of the levers 33 and 34 stores the current position of the carriage 18. The teeth 61 and 62 now sense the correspondingcams 63 and 64 and may encounter a tooth or a recess. The encountering of a tooth signifies that for the corresponding bit there is agreement between the two values relating to the position to be reached and to the current position, while the encountering of a recess signifies that there is' disagreement between these two values. Whichever of the levers 33 and 34 relating to a bit having a value agreeing with that of the current position is not stopped by thelug 27 is nevertheless stopped in its turning action by the tooth of the corresponding cam 63 or 64, as a result of which both the projections 107 and 114 of the levers 33 and 34 remain above 'the paths of the lugs 106 and 113 of the levers 92 and 109. On the other hand, one of the two levers 33 and 34 relating to a bit having a value disagreeing with that of the current position continues its turning action and bring its projection 107 or 114 into the paths of the lugs 106 or 113. If the bit for the desired position is 1 and the bit for the actual position is 0, the projection 107 of the lever 33 moves into the path of the corresponding lug 106. If the bit for the desired position is 0 and the bit for the actual position is 1, the projection 114 of the lever 34 moves into the path of the corresponding lug 113.

Immediately afterwards, the cams 101 and 102 on the shaft 52 cause the bail 97 to turn anticlockwise and release the levers 92 from the universal bar 96. Under the action of the springs 94, the levers 92 tend to follow the rotation of the bail 97 and obviously cause the levers 109 attached to them to move with them. Let it be assumed first of all that the carriage 18 is to perform a tabulating movement or travel from left to right, for example from the zero position of FIG. 1 to position 12, indicated in code 0001100. The number corresponding to the position to be reached is therefore greater than that corresponding to the current position. Comparison between the two numbers is effected by comparing the individual bits, starting from the bit of higher weight, through the medium of the levers 92 and 109.

If the projections 107 and 114 relative to the same bit are both raised, the bit relative to the position to be reached has the same value as the bit relative to the current position. The bit of greater weight having a different value in the two numbers will be one for the position to be reached and zero for the current position. In the example given, this bit is that of weight 8. The lug 106 of the fourth lever 92 from the bottom in FIG. 2, that is of the lever 92 relating to this bit, encounters the corresponding projection 107, as a result of which the lever 92 is stopped. Because of the engagement of the shoulders 104 with the lugs 103, all the levers 92 relative to the bits of lower weight are arrested. These levers 92 therefore remain substantially in the position of FIG. 4 together with the levers 109 without affecting the bar 116. The levers 92 relating to the bits of weight higher than the bit of weight 8, on the other hand, turn anticlockwise together with the corresponding levers 109 and also do not affect the bar 116. The cranks 117 and 118 (FIG. 7) therefore remain stationary in the position of FIG. 7, with the arm 123 in the path of the lug 124. i

Thereafter, the cam 131 (FIG. 7) permits the bail 126 to turn anticlockwise owing to the action of the spring 129, but the bail 126 is immediately stopped by the arm 123 through the medium of the lug 124. The connecting rods I36 and 223 (FIG. 10) therefore remain substantially in the position shown in the drawings, so that the pin 141 (FIG. 7) of the connecting rod 136 remains engaged in the notch 142 of the lever 143 and the pin 227 (FIG. 10) of the connecting rod 223 remains engaged in the notch 228 of the lever 229.

Immediately afterwards the cam 146 (FIG. 7) on the shaft 52 permits the lever 143 to turn anticlockwise. The connecting rod 136 is now shifted to the right by the lever 143 through the medium of the pin 141 and causes the crank 138 to rotate clockwise together with the shaft 139 and the crank 156 (anticlockwise in FIG. 9). By means of the pin 157, the crank 156 shifts the coupling 159 to the left in FIG. 9 and causes the dogs 173 to mesh with the toothed rim 176 of the sleeve 177, thus rendering this sleeve fast with the shaft 161 and selecting forward movement of the carriage.

At the same time, under the action of the cams 233 and 234 (FIG. 10) on the shaft 52, the lever 229 is turned clockwise and shifts the connecting rod 223 to the right by means of the pin 227. The lever 226 is turned anticlockwise and moves the two pawls 303 and 304 to the right. The lever 226 moreover shifts to the left the connecting rod 312, which engages the pin 318 of the lever 321 by means of the projection 316. Finally, the lever 226 shifts to the left the connecting rod 369, the projection 367 of which acts on the pin 363 and causes the lever 361 to turn clockwise. The shoulder 362 is thus brought above the lug 352 of the lever 60, which has meanwhile been restored by the cam 354. The lug 55 is thus held in the path of the tooth of the clutch 57.

Thereafter, the earns 49 and 51 (FIG. 4) on the shaft 52 cause the cranks 42 to turn anticlockwise through the lever 44 and the connecting-rod 43, as a result of which the bar 41 212 on the pin 213, causes the lever 214, and therefore the spindle 216 and the lever 217, to turn anticlockwise. Through the medium of the groove 219, the pin 218 of the lever 217 shifts the sleeve 188 to the rear, thus disengaging the tooth 193 from the crown wheel 194. The sleeve 188 is therefore disengaged from the shaft 189 of the step-by-step advancing device.

The cams 266 and 267 (FIG. 5) on the shaft 52 then rotate the lever 262 anticlockwise, moving the connecting rod 261 to the left. The cranks 258 are turned anticlockwise, thereby releasing the levers 251 and 252 from the universal bar 257. The springs 256 now tend to cause the levers 251 and 252 to turn anticlockwise and they are arrested selectively by the shoulders 32 of the lugs 27. The levers 251 and 252 which continue to turn are those which represent, in code, the position to be reached. In the case being examined, the levers able to turn are the levers 252 for the bits of weight 64, 32, 16, 2 and 1 and the levers 251 for the bits of weight 8 and 4.

The profiles of the cams 276a to 276g and 277a to 277g in correspondence with the rollers 273 and 274 represent, in code. thecurrent position of the carriage 18. The rollers 273 and 274 which sense the corresponding cams 276a to 276g and 277a to 277 g encounter selectively-a tooth or a recess. The encountering of a tooth signifies that for the bit of that weight there is agreement between the two values relative to the position to be reached and to the current position, while the encountering of a recess signifies that there is disagreement between the two values. If the bit of a given weight has the same value for the position to be reached and the current position of the carriage 18, the projections 281 and 282 of the corresponding pair of levers 251 and 252 are both out of the path of the edge 280 of the bail 283. If this value is different, one of the projections 281 and 282 is brought into the path of the edge 280. In the example under examination, the levers 252 for the bits of weight 16, 32, and 64 are free to turn so far as the lugs 27 are concerned but encounter a tooth in the corresponding cams 277g 02771: and remain with the projection The driving shaft 163 (FIG. 9) now causes the shaft 161 to rotate anticlockwise through the friction clutch 162. The sleeve 177 therefore rotates the gear 183 together with the shaft 184 clockwise. By means of the gear 187 and the cylinder 191, the toothed cylinder 186 rotates the gear 192 clockwise together with the drum 76 and the shaft 66. This direction is indicated in FIG. 10 by an arrow TAB. Thus, by means of the wires 81 and 82, the drum 76 (FIG. 1) moves the carriage 18 to the right. The shaft 66 (FIG. 5), in turn, causes the cams 63a to 63e, 64a to 64a and also the cams 276a to 276e, 277a to 2772 to rotate. Moreover, through the medium of the Geneva motion, the shaft 66 causes the sleeve 67 to rotate intermittently together with the cams 63f, 63g, 64f, 64g, 276f, 276g and 277]", 2773. The cams 276a- 276 and 277a- 277g are explored by the corresponding rollers 273, 274 during the movement of the carriage 18. As the carriage 18 advances, the cams 276a276g and 277a-277g relative to the bits of weight lower than that which has produced the arrest of the edge 280 alternate their teeth and recesses in correspondence with the rollers 273 and 274. The latter can be moved by the inclined flanks of the teeth of the cams, whereby they follow the profiles of the corresponding cams exactly. When the carriage passes from position 7 to position 8, the cam 276d brings one of its teeth into engagement with the roller 273, as a result of which the corresponding lever 251 is turned clockwise, the corresponding .lever 252 being prevented from anticlockwise movement by the lug 27. Simultaneously, the cam 2760 brings a recess in front of the corresponding roller 273, as a result of which the lever 251 relative to the bit of weight 4 brings its projection 281 into the path of the edge 280. The ball 283 performs a small rotation anticlockwise and now bears against the projection 281 relating to the bit of weight 4.

When the carriage passes from position 11 to position 12, the projection 281 relating to the bit of weight 4 is brought out of engagement with the edge 280.

The cams 277a and 277b in correspondence with the respective rollers 274 pass from a recess to a tooth, so that the corresponding levers 252 bring their projections 282 out of the path of the edge 280. Since the levers 251 of the bits of weight 1 and 2 are held by the lugs 27, the bail 283 can now turn further anticlockwise. It is to be noted that during the movement of the carriage 18 described above the levers 251 and 252 relative to the bits of weight greater than 8 have not undergone any consequential movement. It is therefore clear that when the profiles of the cams 276a -276 and 27711 277g in correspondence with the rollers represent in code the 282 out of the path ofthe edge 280. The levers 251 for the bits of weight four and eight are also free to turn so far as the lugs 27 are concerned and what is more they encounter a recess in the corresponding cams 2760 to 276d and therefore do turn and bring the projections 281 into the path of the edge 280.

The cam 296 on the shaft 52 now allows the lever 293 to rotate clockwise owing to the action of the spring 294. The connecting rod 292 is thus shifted to the right and allows the bail 283 to turn anticlockwise. Since the edge 280 (FIGS. 2 and 3) is stepped, this edge encounters the projection 281 of the turned lever 251 relating to the bit of greater weight, that is, in the example given, that relating to the bit of weight 8.

Thereafter, the cams 376 and 377 (FIG. 8) on the shaft 52 cause the lever 381 to turn anticlockwise, thereby shifting the connecting rod 383 to the right. The crank 384 is now rotated clockwise, together with the spindle 386 and the crank 387,

which moves the link 389 (FIG. 9) downwards. The latter causes the lever 396 to turn clockwise and the bail 403 to turn anticlockwise. The arm 404 now presses against the disc 407 through the medium of the roller 406, while the lever 398 presses against the disc 408 through the medium of the roller 401, thereby producing the closing or engagement of the friction clutch 162.

Finally, the clutch 57 (FIG. 10) is disengaged by the lug of the lever 60. The shaft 52 is thus stopped after rotating through 180.

position that the carriage 18 is to reach, the levers 251 and 252 are all turned clockwise.

By means of the connecting rod 297 (FIG. 10) the bail 283 now rotates the lever 298, which releases the pawls 303 and 304 from the stud 301, allowing them to engage the corresponding toothed wheels 306 and 307. The two pawls 303 and 304, which, as has already been seen, have been shifted to the right, engage the two teeth of the wheels 306 and 307 to be arrested in this shifted position. Since the shaft 66 rotates anticlockwise, the pawl 303 is engaged by the wheel 306 and shifted further to the right, while the pawl 304 drops to the left of the tooth of the wheel 307, preventing rebound thereof at the instant of arrest. The lever 226 is therefore rotated together with the shaft 66.

The connecting rod 312 is now shifted to the left and causes the lever 321 to turn anticlockwise, thereby actuating the dash-pot 323, which damps the travel of the carriage 18 and therefore the rotation of the shaft 66, while the friction clutch 162 (FIG. 9) begins to slip.

Moreover, since the lever 226 turns anticlockwise, it causes the lever 229 to turn clockwise by means of the connecting rod 223 and brings it to bear against the recess 236 of the cam 233.

The rotation of the lever 226 causes the connecting rod 369 to move further to the left, so that the projection 367 causes the lever 361 to turn further clockwise, in such manner that 11 I the shoulder 362 is brought to the left of the lug 352 of the lever 60. The clutch 57 is thus reengaged. for a second cycle of the shaft 56, whereby the shaft 52 initiates another rotation through 180.

At the beginning of this second rotation, the cams 376 and 377 (FIG. 8) on the shaft 52 cause the lever 381 to turn clockwise and, by means of the connecting rod 383, the lever 381 turns the crank 384 anticlockwise. The spindle 386 and the crank 387 also turnanticlockwise and push the link 389 (FIG. 9) upwards. Through the connecting links 393 and 394, the lever 396 and the bail 403 are turned clockwise and anticlockwise, respectively, sureon the disc 408 and the friction clutch 162 is disengaged.

Thereafter, the cams 266 and 267 (FIG. on the shaft 52 cause the lever 262 to turn clockwise and therefore move the connecting rod 261 to the right. The cranks 258 turn clockwise and, by means of the bar 257, bring the levers 251, 252 back into the inoperative position. In turn, the cam 146 (FIG. 7) on the shaft 52 returns the lever 143 to the inoperative position and, the connecting rod 136 back to the left until it is in the position'shown in the drawing. The spindle 139 and the crank 156 (FIG. 9) are rotated clockwise and, by means of the pin 157 bring the coupling 159 back into the inoperative central position,'disengaging it from the sleeve 177.

Moreover, the cams 233, 234 (FIG. cause the lever 229 to turn anticlockwise, as a result of which theconnecting rod 223 is moved to the left and causes the lever 226 and, therefore, through the medium of the pawl 303, the shaft 66 to turn clockwise. Through the drum 76 and the wires 81 and 82 (FIG. 1), this movement of shaft 66 corrects the overshoot in the position of the carriage 18 which has been identified by the cams 276a276g and 277a277g.

Finally, the cam 201 (FIG. 8) allows the lever 202 to turn clockwise, bringing the link 204 upwards and allowing the lever 208 (FIG. 9) to turn clockwise under the action of the spring 211. Due to the action of the cam slot 212 on the pin 213, the lever 214 rotates clockwise and causes the spindle 216 and the lever 217 also to rotate clockwise. The pin 218 therefore moves the sleeve 188 forward and brings the tooth 193 into engagement with the crown wheel 194. The shaft 66 is thus. reconnected to the step-by-step advancing device while the position of the carriage 18 is further corrected.

The cam 296 (FIG. 5) rotates the lever 293 anticlockwise, shifting to-the left the connecting rod 292, which brings the bail 283 back to the inoperative position. The bail 283 now moves downwards the connecting rod 297 (FIG. 10), which causes the lever 298 to turn clockwise, as a result of which the pawls 303 and 304 are disengaged from the corresponding wheels 306 and 307.

In turn, the cam 354 (FIG. 10) on the shaft 56 brings the lug 55 of the lever 60 back into the path of the release tooth of the clutch. The rotation of the lever 226 by means of the connecting rod 369 allows the lever361 to turn anticlockwise as far as the inoperative position. The cam 343 causes the lever 341 to ,turn clockwise and, by means of the pin 339, causes the lever 336 to turn anticlockwise. The lever 348 follows the rotation of the lever 336 and brings the shoulder 349 back into the path of the lug 352 of the lever 60, which is thus held in position.

The release tooth of the clutch 57 is now engaged against the lug 55 of the lever. 60. The clutch 57 is opened or disengaged and thus terminates the tabulating operation.

The start 'electromagnet 330 has meanwhile been deenergized. The spring 334 has therefore been holding the lug 335 bearing against the edge of the lever 336. The pallet 331 can now turn anticlockwise until it bears against the stop 333. The lever 336 is thus held in the position shown in the drawing.

Let it now be assumed that the carriage 18 (FIG. 1) is to perform a tabulating motion from right to left, for example from position '12 which has now been reached, indicated in code by. 0001 100, to position 3, indicated in code by 0000011. The number corresponding to the position to be reached is so that the roller 401 ceases its pres-.

therefore, by means of the pin 141, brings therefore lower than that corresponding to the current position.

The bit of greater weight having a different value in the two numbers will be one for the current position and zero for the position to be reached. In the example given, this bit is again that of weight 8. When the universal bar 96 releases the levers 92, the lug 113 (FIG. 4) of the lever 109 relating to this The now encounters the projection 114 of the corresponding lever 34. Since the spring 94 prevails over the spring 111, the lever 92 continues its rotation, thus causing the lever 109 to turn clockwise about the pin 108. The lever 109 acts on the bar 116 and causes the cranks 117 and 118 (FIG. 7) to turn anticlockwise, thereby taking the arm 123 out of the path of the lug 124.

The levers 92 and the levers 109 relating to the bits of weight greater than 8 continue anticlockwise rotation without encountering the corresponding projections 107 and 114. The lever 109 relating to the bit of weight 4 encounters the corresponding projection 114 and turns in a manner similar to that of weight 8. Finally, the levers 92 and 109 relating to the bits of weight 2 and 1 also continue anticlockwise rotation without encountering the corresponding projections 107 and 114. It is therefore clear that when the position to be reached is to the left of the current position, at least the lever 109 relative to the bit of greater weight having a different value acts on the bar 116.

Now when the cam 131 (FIG. 7) allows the bail 126 to turn anticlockwise, the bail 126 is no longer arrested by the arm 123 and, by means of its arm 133 and the link 134, causes the connecting rod 136 to rotate clockwise. The pin 141 is therefore disengaged from the notch 142 of the lever 143, while the pin 148 engages in the notch 149 of the lever 151. The arm 221 of the bail 126 causes the connecting rod 223 to turn clockwise by means of the link 222 (FIG. 10), thereby disengaging the pin 227 from the notch 228 of the lever 229 and engaging the pin 237 in the notch 238 of the lever 239.

Thereafter, the cam 153 (FIG. 7) on the shaft 52 allows the lever 151 to turn clockwise. The connecting rod 136 is now moved to the left and causes the crank 138 to turn anticlockwise and, through the medium of the spindle 139, the crank 156 (FIG. 9) and the pin 157, said crank 138 shifts the coupling 159 to the right in the drawing. The ring 172 therefore engages with the toothed rim 178 of the sleeve 179, so that the latter is now fast in rotation with the shaft 161.

29 said crank 138 shifts the coupling 159 to the right in the drawing. The ring 172 therefore engages with the toothed rim 178 of the sleeve 179, so that the latter is now fast in rotation with the shaft 161.

At the same time, under the action of the cams 243 and 244 (FIG. 10), the lever 239 is turned anticlockwise and shifts the connecting rod 223 to the left. The lever 226 is therefore rotated clockwise and shifts the two pawls 303 and 304 together with it to the left in the drawing. The lever 226 moreover moves to the right the connecting rod 312 which, through the medium of the projection 317, is brought into contact with the stud 319, of the lever 321. Finally, the lever 226 shifts to the right the connecting rod 369, the projection 368 of which acts on the pin 364 and causes the lever 361 to turn clockwise as in the preceding case. As has already been described, the shoulder 362 is thus brought above the lug 352 of the lever 60, keeping the lug 55 in the path of the tooth of the clutch 57, as a result of which the shaft 56 will be arrested after a complete revolution.

The levers 33 and 34 (FIG. 4) and the levers 92 and 109 are then brought back to the inoperative position, while the sleeve 188 (FIG. 9) is disengaged from the step-by-step advancing device as in the preceding case. In turn, the levers 251 and 252 (FIG. 5), which are released by the universal bar 257, are arrested selectively by the shoulders 32 of the lugs 27 and those which continue to rotate represent afresh the position to be reached.

In the example under examination, the lugs 27 allow the rotation of the levers 251 for the bits of weight 1 and 2 and of the levers 252 for the bits of weight'4, 8, 16, 32 and 64. The levers 251 for the bits of weight 1 and 2 encounter recesses in the cams 276a and 2761: (see also FIG. 12), the levers 252 for the bits of weight 4 and 8 encounter recesses in the cams 2770 and 277d and the levers 252 for the bits of weight 16, 32 and 64 encounter a teeth of the cams 277e, 277fand 277g.

When the bail 283 then turns anticlockwise, the edge 280 (FIGS. 2 and 3) now encounters the projection 282 of the lever 252 relating to the bit of weight 8, that is of the rotated lever 252 relating to the bit of greater weight. Thereafter, the friction clutch 162 (FIG. 9) is engaged as in the preceding case, so that driving'shaft 163. via the friction clutch 162, the shaft 161 and the sleeve 179, now causes the shaft 184 to rotate anticlockwise. The gear 192 is therefore rotated anticlockwise together with the drum 76 and the shaft 66, on which this direction is indicated by the arrow R, for Return. Through the medium of the wires 81 and 82 the drum 76 (FIG. 1) therefore moves the carriage 18 to the left. The shaft 66 (FIG. 5), in turn, causes the cams 63a-63e, 6 4a64e and also the cams 276a276e, 277a277e to rotate, while the shaft 66 causes the sleeve 67 to rotate intermittently together with the cams 63f, 63g, 64g, 276f, 276g and 277f, 277g in the opposite direction to that ofthe preceding case.

As the carriage 18 moves back, the'cams 276a-276g and 277a277g relating to the bits of weight lower than that which has produced the arrest of the edge 280 alternate their teeth and recesses in correspondence with the rollers 273 and 274. When the carriage passes from position 8 to position 7, the cam 277d brings one of its teeth into engagement with the roller 274, as a result of which the corresponding lever 252 is turned clockwise, the corresponding lever 251 being held in a turned condition by the lug 27. Simultaneously, the cam 277c brings a recess in front of the corresponding roller 274, as a result of which the lever 252 relating to the bit of weight 4 brings its projection 282 into the path of the edge 280. The bail 283 performs a small rotation anticlockwise and now bears against the projection 282 relating to the bit of weight 4.

Finally. when the carriage passes from position 4 to position 3. the projection 282 relating to the bit of weight 4 is brought out of engagement with the edge 280. The cams 276a and 276b in correspondence with the respective rollers 273 pass from a recess to a tooth, so that the corresponding levers 251 bring their projections 281 out of the path of the edge 280.

Since the levers 252 of the bits of weight 1 and 2 are held by the lugs 27, the bail 283 can now turn further anticlockwise, as the levers 251 and 252 are now all turned clockwise.

The bail 283 releases the pawls 303 and 304 (FIG. 10) in the manner already described, allowing them to engage the corresponding toothed wheels 306 and 307. The two pawls 303 and 304 which, as has already been seen, have been moved to the left, engage the two teeth of the wheels 306 and 307 to be arrested in this shifted position. Since the shaft 66 now rotates clockwise, the pawl 304 is engaged by the wheel 307 and shifted further to the left, while the pawl 303 drops to the right of the tooth of the wheel 306 to prevent any rebound at the instant of arrest. The lever 226 is thus turned afresh together with the shaft 66.

The connecting rod 312 is now shifted to the right and causes the lever 321 to turn anticlockwise again to actuate the dash-pot 323 as in the preceding case. Moreover, by turning clockwise, the lever 226 causes the lever 239 to turn anticlockwise by means of the connecting rod 223, bringing the lever 239 to bear against the recess 246 of the cam 243. The rotation of the lever 226 causes the connecting rod 369 to move further to the right, as a result of which the projection 368 turns the lever 36] further clockwise. The shoulder 362 is thus brought to the left of the lug 352 of the lever 60, as a result of which the clutch 57 is reengaged for a second cycle of the shaft 56 and the shaft 52 initiates a further rotation through 180.

At the beginning of this rotation, the friction clutch 162 (FIG. 9) is disengaged and the levers 251 and 252 (FIG. 5) are brought back to rest. Thereafter, the cam 153 (FIG. 7) of the shaft 52 brings the lever 151 back into the inoperative position and, therefore, by means of the pin 148, brings the connecting rod 136 back into the position shown in the drawing. By means of the crank 156 (FIG. 9), the spindle 139 brings the coupling 159 back into the central position, disengaging it from the sleeve 179.

Moreover, the cams 243 and 244 (FIG. 10) cause the lever 239 to turn clockwise, so that the connecting rod 223 is shifted to the right and causes the lever 226 and, via the pawl 304, the shaft 66 to rotate anticlockwise, as a result of which the position of the carriage 18 identified by the cams 276a- 276g and 277a-277g is corrected through the drum 76 and the wires 81 and 82 (FIG. 1) in a similar manner to the preceding case. Finally, the tooth 193 (FIG. 9) reengages with the crown wheel 194, which reconnects the carriage 18 to the step-by-step advancing device.

In the last part of the cycle of the shaft 52, the bail 283 (FIG. 5) is brought back to the inoperative position and causes the pawls 303 and 304 to be disengaged from the wheels 306 and 307.

Moreover, the cam 131 (FIG. 7) causes the bail 126 to turn clockwise, bringing it back into the position shown in tl1e drawing. The link 134 causes the connecting rod 136 to turn anticlockwise, as a result of which the pin 148 is disengaged from the notch 149 and the pin 141 is reengaged in the notch 142. The link 222 (FIG. 10), in turn, causes the connecting rod 223 to turn anticlockwise, as a result of which the pin 237 is disengaged from the notch 238 and the pin 227 is reengaged in the notch 228. Moreover, the lug 124 (FIG. 7) is moved out of the path of the arm 123, so that the lever 118 is returned by the spring 121 to the position shown in the drawing. In consequence of the return of the lever 226 in an anticlockwise direction, the lever 361 also returns in an anticlockwise direction and the tabulating operation from right to left terminates in an identical manner to that from left to right.

MOVEMENT OF THE CARRIAGE OUTSIDE THE TABULATING RANGE The carriage 18 (FIG. 1) can pass beyond the zero position and position 127 by means of the step-by-step advancing device or by manual movement. In these positions, hereinafter called the extramarginal positions the cams 63a-63e; 64a- 64e; 276a-276e and 277a-277e (FIG. 12) on the shaft 66 present in front ofthe relative teeth 61, 62 (FIG. 4) and of the rollers 273, 274 (FIG. 5) a portion of their profile which is repeated cyclically. On the other hand, the cams 63f, 63g; 64f, 64g; 276f, 276g and 277]", 277g (FIG. 12) on the sleeve 67 present to the teeth 61, 62 and to the rollers 273, 274 a portion of their profile outside the 240 corresponding to the movement of the carriage 18 from the zero position to position 127. To this end, the cams on the sleeve 67 are shaped in this portion in a manner similar to the said 240.

Moreover, the sleeve 67 carries another pair of cams 411 and 412 (FIG. 11), the cam 411 being provided with a single tooth which extends from the zero position to beyond position 127 over an arc corresponding to the extramarginal travel of the carriage 18 to the right. The cam 412, on the other hand, has a tooth which extends from position 127 beyond the zero position over an arc corresponding to the extramarginal travel of the carriage 18 to the left. The two cams 411 and 412 can be sensed by two'levers 413 and 414, respectively, pivoted on the spindle 38 and normally bearing under the action of two springs 416 against the universal bar 41.

The lever 413 is provided with a tooth 418 for reading the cam 411 and with a projection 421 adapted to cooperate with a lug 423 ofa lever 426 fulcrumed on the spindle 93. The lever 414, in turn, is provided with a tooth 419 for reading the cam 412 and with a projection 422 adapted to cooperate with a lag 424 carried by a lever 427 pivoted on a pin 428 of the lever 426. Normally, the lever 426 bears under the action of a spring 429 against the universal bar 96 and the lever 427 bears under the action ofa spring 431 against a stud 432 fixed to the Finally, the sleeve 67 carries another cam 441 having a tooth extending over the arc of 240 corresponding to the movement of the carriage 18 from the zero position to position 127. The cam 441 is adapted to be sensed by a roller 442 of a lever .443 pivoted on the spindle 38 and normally bearing under the action of a spring 444 against the universal bar 257. The lever 443 is provided with a projection 446 adapted to cooperate with the edge 280 ofthe bail 283.

Let it now be assumed that the carriage 18 (FIG. 1) is located beyond the zero position and is to perform a tabulating travel, for example from position -5 (to the left of the zero position) to position 125, represented in code by 1111101. To order the movement, similarly to what has been seen before, the program sends a first group of signals which set the code bars 26 (FIG. 6) and another signal energizing the start electromagnet 330, in response to which the clutch 57 is engaged and produces a 360- cycle of the main shaft 56 and a rotation of the shaft 52 through-180.

At the beginning of the cycle, when the two earns 49 and 51 (FIG. 4) on the shaft 52 cause the lever 44 to turn clockwise, the universal bar 41 releases, in addition to the levers 33 and 34 which are arrested selectively by the shoulders 31' of the lugs 27, the levers 413 and 414 (FIG. 11), which both rotate until they bear against the corresponding cams 411 and 412, In the case under examination, the leve -.413 encounters the recess of the cam 411 and therefore brings the projection 421 into the path of the lug 423 of the lever 426, while the lever 414 encounters the tooth of the cam 412, as a result of which it is arrested with the projection 422 out of the path of the lug 424 of the lever 427. The teeth 61 and 62 (FIG. 4) now sense the correspondingcams 63a-63g and 64a-64g and may encounter a tooth or a recess.

Immediately afterwards, when the cams 101 and 102 cause the bail97 to turn anticlockwise, theuniversal bar 96 releases, in addition to the levers 92, also the lever 426 (FIG. 11). Under the action of the spring 429, this lever tends to follow the bail 97 together with the lever 427.

In the example under examination, the lug 423 of the lever 426 encounters the projection 421 of the lever 413, as a result of which the lever 426 is stopped. Because of the engagement of the shoulder 433 with the lug 103 of the lever 92 relating to the bit ofweight 64, all the levers 92 are stopped, as a result of which the bar 116 is not affected by the levers 109 and 427. The bail 126 accordingly does not turn and the teeth 173 (FIG. 9) are therefore brought into engagement with the toothed rim 176 ofthe sleeve 177, as in the case of the tabulation from left to right.

Thereafter, the cams 49 and 51 (FIG. 4) on the shaft 52 return both the levers 33, 34 and the levers 413 and 414 to the inoperative position. while the cams 101 and 102 return the lever 426 and the lever 427 to the inoperative position, together with the levers 92 and 109. Simultaneously, the cam 201 (FIG. 8) causes the sleeve 188 to be disengaged from the step-by-step advancing device.

Thereafter, when the cams 266and 267 (FIG. 5) cause the cranks 258 to turn anticlockwise, the universal bar 257 releases, together with the levers 251 and 252, also the lever 443. In the case under consideration, under the action of the spring 444, the lever 443 turns anticlockwise until it bears against the recess olthe cam 441. thus bringing the projection 446 into the path of the edge 280 of the bail 283. Moreover, the levers 251 for the bits of weight 64, 32, 16, 8, 4 and 1 and the lever 252 for the bit of weight 2 can turn until they bear against the respective cams. The edge 280 of the bail 283 now encounters the projection 446 ofthe lever 443.

The friction clutch 162 (FIG. 9) is thereupon closed or engaged, as a result of which the carriage 18 begins to move to the right in a manner similar to that seen before. When the carriage 18 reaches position 3, to the left of the zero position, the rollers 273 and 274 of the levers 251 and 252 which are turned are located in correspondence with a tooth of the respective cams 276a, 276b276g and 277b (FIG. 12). The

respective projections 281 (FIG. 5) and 282 of said levers 251 and ,252 are therefore all brought out of the path of the edge 280 of the bail 283. The profile of the cams 276a276g and 277a-277g (FIG. 12) in correspondence with this position of the carriage 18 is therefore the same as the cams have in correspondence with position 125. The cam 441 ensures unambiguous determination of the position of the carriage and the representation in code supplied by the cams also for the extramarginal positions.

' When the carriage 18 passes from position 1 to the left of the zero position, to the zero position, the tooth of the cam 441 engages the roller 442, which causes the lever 443 to turn clockwise, as a result of which the projection 446 is brought out of the path of the edge 280. Simultaneously. however, the rollers 273 of the levers 251 relating to the bits of weight 64, 32, 16', 8, 4 and 1 are all located in a recess of the respective cams and bring their projections 281 into the path of the edge 280, which is arrested by the projection 281 relating to the bit of weight 64. From this point onwards, the operation proceeds like a normal tabulating operation from left to right.

Finally, let it be assumed that the carriage 18 (FIG. 1) is located beyond position 127 and is to perform a tabulating travel, for example from position 133, six to the right of position 127 to position 2, represented in code by 0000010. When the universal bar 41 (FIGS. 4 and 11) releases the levers 33,

' 34 and 413, 414, the lever 413 now encounters the tooth of the cam 411 and the lever 414 encounters the recess of the cam 412. The projection 421 of the lever 413 therefore remains out of the path of the lug 423 of the lever 426, while the projection 422 of the lever 414 is brought into the path of the lug 424 of the lever 427.

When the bail 97 is then turned anticlockwise, the lever 426 can also turn anticlockwise, while the lug 424 encounters the projection 422. The lever 427 is therefore turned clockwise about the pin 428 and engages the bar 116, causing the cranks 117 and 118 (FIG. 7) to turn and thus moving the arm 123 out of the path of the lug 124 of the bail 126, as in the case described before the tabulation from right to left.

Thereafter, when the levers 251, 252 (FIG. 5) and the lever 443 (FIG. 11) are released by the universal bar 257, the lever 443 turns anticlockwise until it bears against the recess of the cam 441, bringing the projection 446 into the path of the edge 280. Moreover. the levers 252 for the bits ofweight 64, 32, 16, 8, 4 and 1 and the lever 251 for the bit of weight 2 turn until they bear against the corresponding cams. The edge 280 of the bail 283 is thus arrested by the projection 446 of the lever 443,

The clutch 57 (FIG. 10) is then disengaged, while the friction clutch 162 (FIG. 9) is engaged. The driving shaft 163 now causes the drum 76 and the shaft 66 to rotate in the direction of the arrow R and causes the carriage 18 to be shifted to the left. When the carriage 18 reaches position 3 to the right of position 127, the projection 281 and 282 of the turned levers 251 and 252 are all brought out ofthe path ofthe edge 280. In fact, the profile of the cams 276a-276g and 277a277g (FIG. 12) in correspondence with this position of the carriage 18 coincides with the profile of the same cams in position 2. The bail 283 therefore remains supported exclusively by the projection 446 of the lever 443, which is still in the recess of the cam 441.

When the carriage 18 passes from position 128 to position 127, the tooth of th e'cam 441 engages the roller 442 of the lever 443, so that the projection 446 is brought out of the path of the edge 280. Simultaneously, however, the rollers 274 of the levers 252 for the bits of weight 64, 32, 16, 8, 4 and l are all located in a recess. The bail 283 is thus arrested by the projection 282 of the lever 252 relating to the bit of weight 64. The carriage 18 then continues its travel and is arrested in position 2 in a manner identical to the case described before the tabulation from right to left.

it is understood that various modifications. improvements, additions or elimination of parts may be effected in the arrangement described without departing from the scope of the invention. For example, all the cams 63a-63g, 6411-645, 276a-276g and 277a-277g may be keyed on a single shaft. Moreover, the cams 63a63g and 64a64g and the relative levers 33 and 34 could be eliminated by causing the levers 92 and 109 to sense the levers 251 and 252 directly. Finally, instead of pairs of complementary cams, it would be possible to use a single series of cams adapted to be suitably sensed in such manner as always to give a positive mechanical signal.

We claim:

1. A tabulating mechanism for an accounting machine comprising; 1

a carriage movable transversely of the machine;

a support for paper;

a printing device mounted on said carriage, the relative position of said device with respect to said support being changeable upon movement ofthe carriage;

a first storage unit for indicating the current position of the carriage;

a second storage unit for indicating the desired position of the carriage;

means for comparing the indications provided by said first and second storage units; and

driving means controlled by said comparing means for moving the carriage until the indications provided by the first and second storage units are equal.

2. A tabulating mechanism as recited in claim 1, wherein said first and second storage units comprise means for representing said current and desired positions, respectively, in codes comprising combinations of binary units.

3. A tabulating mechanism as recited in claim 2, wherein said representing means for said first storage unit comprises a plurality of pairs of partsfor representing the two states of each binary unit of a current position code, and wherein said representing means for said second storage unit comprises a plurality of members having two positions for representing the two states of each binary unit of a desired position code, and wherein said comparing means comprises a plurality of pairs ofelements for sensing said parts and said members simultaneously and thereby comparing said current-and desired position codes.

4. A tabulating mechanism as recited in claim 3, wherein the parts of each of said pairs of parts are fixedly interconnected; and further comprising means for moving said parts simultaneously with movement of said carriage.

5. A tabulating mechanism as recited in claim 4, wherein each of said pairs of parts comprises a pair of cams having complementary profiles, each said pair of cams indicating for each position ofthe carriage the state of the correspondingbinary unit of said current position code.

6. A tabulating mechanism as recited in claim 5, wherein at least two of said pairs of cams are fixedly interconnected, and wherein said moving means comprises means for-rotation said two pairs ofcams.

7. A tabulating mechanism as recited in claim 6, wherein 1 said moving means further comprises means for intermittently rotating at least an additional one of said pairs of cams, said intermittent rotating means being responsive to each revolution of said two pairs ofcams.

8. A tabulating mechanism as recited in claim 7, wherein said intermittent rotating means comprises a Geneva motion including, a rotatable disc having a plurality of radial slots therein, said slots being spaced apart circumferentially about said disc at 60 intervals, said disc comprising the driven part of said motion, and a rotatably mounted pin engageable with said slots, said pin comprising the driving part of said motion, the distance between said pin and the rotational axis thereof being one-half the distance between the rotational axes of the disc and the pin.

9. A tabulating mechanism as recited in claim 3, wherein one element of each pair ofelements of said comparing means moves into an operative attitude for sensing one part of the corresponding pair of parts of said first storage unit upon sensing the corresponding member of said second storage unit, said one element upon movement into said operative attitude representing the state of the corresponding binary unit of said desired position code.

10. A tabulating mechanism as recited in claim 9, wherein said one element upon movement into said operative attitude adopts one of two positions according to the position of said one part sensed, the first of said two positions signifying that said current and desired position codes are equal for the corresponding binary unit, and the second of said two positions signifying that said current and desired position codes are different for the corresponding binary unit.

11. A tabulating mechanism as recited in claim 10, further comprising stop means responsive to the elements of said comparing means for stopping the carriage when all of the binary units of said current and desired position codes as indicated by said first and second storage units. respectiveiv. are equal.

12. A tabulating mechanism as recited in claim 11, wherein the stop means comprise, a pair of pivotally mounted pawls and a pair of rotatably mounted, fixedly interconnected, toothed wheels, each of said pawls being movable from an inoperative to an operative position and in said operative position engageable with the teeth of one of said wheels for stopping the rotation thereof, the teeth of one said wheels being slanted oppositely to the teeth of the other of said wheels so that one of said pawls is operative to stop the rota tion of the associated wheel in one direction and the other of said pawls is operative to stop the rotation of the associated wheel in the opposite direction, said pawls thus forming a stop and counterstop for said wheels, and means for simultaneously rotating the wheels with movement of the carriage.

13. A tabulating mechanism as recited in claim 12, wherein said driving means comprises a rotatably mounted drum, a pair of wires wound on said drum and connected to opposite sides of the carriage for moving the carriage transversely of the machine upon rotation of said drum, and means for rotating said drum.

14. A tabulating mechanism as recited in claim 13, wherein said wheels are fixedly connected to said drum, and wherein said pawls are carried by a pivotally mounted lever, said lever being mounted coaxially of said drum and operatively connected to said comparing means for pivotal movement from an inoperative attitude to one of two operative attitudes, said two operative attitudes corresponding to the two directions of movement of the carriage.

15. A tabulating mechanism as recited in claim 14, wherein said pawls are moved from said inoperative position to an intermediate position upon movement of said lever to one of said two operative attitudes, and wherein said stop means further comprises a fluid damper operatively connected to said lever so that when the pawls are moved to said operative position and engage the teeth of said wheels, the lever will be further pivotally moved and said damper will be actuated,

16. A tabulating mechanism as recited in claim 3, wherein said driving means includes means for determining the desired direction of carriage movement.

17. A tabulating mechanism as recited in claim 16, wherein said determining means comprises a plurality of pairs of reading elements associated with said pairs of sensing elements, each said reading element being operative to read the associated sensing element after the sensing element has sensed the corresponding part ofthe first storage unit.

sensing element while said other lever of said one pair of levers is not arrested by'the associated sensing element and for causing the carriage to move in the opposite direction when none of said one levers is arrested by the associated sensing element.

19. A tabulating mechanism as recited in claim 18, wherein said determining means further comprises a shoulder mounted on each of said other levers and a lug also mounted on each of said other levers, said shoulder of one of said other levers being operative to engage said lug of said other lever of the binary unit of immediately lower weight so that said one and other levers of said binary unit of said immediately lower weight and binary units of still lower weight will have no affect upon said control means.

20. A tabulating mechanism as recited in claim 19, wherein said determining means further comprises a pair of ring gears corresponding to the two directions of movement of the carriage, and a coupling operatively connected to said control means for selective engagement with one of said ring gears.

. 21. A tabulating mechanism as recited in claim 3, wherein said comparing means comprises two pluralities of pairs of sensing elements; a first plurality of said pairs of sensing elements being operative to simultaneously sense selected pairs of parts of the first storage unit and the members of the second storage unit for controlling the direction of movement of the carriage, and a second plurality of said pairs of sensing elements being operative to simultaneously sense selected pairs of parts of the first storage unit and the members of the second storage unit for controlling the stopping of the carriage when the current and desired positions thereof are equal.

22, A tabulating mechanism as recited in claim 21 wherein each of said pairs of sensing elements comprises a pair of levers, and wherein each of the pairs of parts of the first I storage unit comprises a pair of complementary cams, the

profiles of each of said pairs of cams representing zero and one for the corresponding binary unit for all current positions of the carriage, thepairs of cams sensed by said first pairs of levers alternating with the pairs of cams sensed by said second pairs oflevers.

23. A tabulating mechanism as recited in claim 3, wherein the first storage unit comprises an additional pair of parts for indicating the current position of the, carriage outside the range of desired positions indicatable by the members of the second storage unit. and wherein the comparing means comprises an additional pair of sensing elements for sensing said additional pair of parts and controlling the driving means so that the carriage will be shifted towards a desired position within said range of desired positions indicatable by the second storage unit.

' 24. A tabulating mechanism as recited in claim 23, wherein the first storage unit comprises another additional part; and wherein the comparing means comprises another additional sensing element for sensing said other additional part to an accounting machine comprising,

prevent the carriage from stopping until the carriage is within the desired positions indicatable by the second storage unit.

25. A tabulating mechanism as recited in claim 1, further comprising a cyclic actuating means having an inoperative and an intermediate position, said actuating means in said intermediate position being operative to control said comparing means and said driving means, and returning to said inoperative position when the current and desired position of the carriage are equal.

26. In a mechanism for positioning a movable component of a first storage unit for indicating the current position of said component, a second storage unit forindicating thedesired position of said component, said first and second storage units representing the current and desired positions of said component. respectively, in binary codes, and means for comparing the indications provided by said first and second storage units and effecting movement of said component until said indications are equal, the improvement wherein said first storage unit comprises a plurality of pairs ofdparts for representing the two states of each binary unit, sat second storage unit comprises a plurality of two-position members for representing the two states of each binary unit, and the comparing and movement effecting means comprises a plurality of pairs of sensing elements for sensing said parts and said members simultaneouslyv 27 A mechanism as recited in claim 26, wherein the parts of each of said pairs of parts are fixedly interconnected, and wherein all of said parts are movable simultaneously with said component.

28. A mechanism as recited in claim 27, wherein each of said pairs of parts comprises a pair of cams having complementary profiles for indicating in each position of said component the state ofthe corresponding binary unit.

29. A mechanism as recited in claim 28, wherein at least two of said pairs of cams are fixedly interconnected, and further comprising means for rotating said two pairs of cams simultaneously with movement of said component.

30. A tabulating mechanism for an accounting machine comprising:

a support for paper;

a printing device;

means for changing the relative position of said device with respect to said support including a carriage movable transversely of the machine;

a first storage unit for indicating carriage;

a second storage unit for indicating the desired position of the carriage;

means for comparing the indications provided by said first and second storage units; and

driving means controlled by said comparing means for moving the carriage until the indications provided by the first and second storage units are equal.

the current position of the 

